Variable output gear pump or motor apparatus

ABSTRACT

THIS INVENTION RELATES TO VARIABLE CAPACITY ROTARY HYDRAULIC PUMP AND/OR MOTOR APPARATUS OF THE KIND COMPRISING, MORE PARTICULARLY, A PUMP HAVING A VARIABLE DISCHARGE THAT WILL OPERATE AT A CONSTANT SPEED OR A VARIABLE SPEED MOTOR DRIVEN BY A CONSTANT VOLUME OF FLUID. MORE PARTICULARLY, THIS INVENTION RELATES TO A HYDRAULIC PUMP OR MOTOR HAVING ROTATING, ENGAGING TEETH MEMBERS MOVABLE AXIALLY RELATIVE TO EACH OTHER WITHIN RESPECTIVE SLEEVE PORTIONS TO EXPOSE VARIABLE MESHING TEETH AREAS TO PROVIDE THE EFFICIENT AND EFFECTIVE VARIABLE OUTPUT APPARATUS OF THIS INVENTION. ADDITIONALLY, THIS INVENTION RELATES TO VARIABLE OUTPUT APPARATUS HAVING A CONTROL VALVE OPERABLY CONNECTED TO OPPOSITE SIDES OF THE MESHING GEAR TEETH MEMBERS SO AS TO AUTOMATICALLY MAINTAIN A GIVEN ADJUSTED POSITION AND OPERABLE TO READILY MOVE THE TEETH MEMBERS RELATIVE TO EACH OTHER WHEN DESIRED WITH SAID OF THE OPERATING FLUID PRESSURE.

States Patent {72] Inventor Lowell E. Bur-1t Box 36, Oakley, Karts.67748 [21] Appl. No. 854,122 [221' Filed Aug. 29,1969 [45] Patented June2%, 1971 [54] VARIABLE OUTPUT GEAR PUMP 01R MOTOR APPARATUS 5 Claims,9Drawing Figs.

[52] 11.5.01 410/211 [51] Int. (11. l 1 Mlle 21/16 [50] Field cl Search103/120,

[56] References Cited UNITED STATES PATENTS 1,223,734 4/1917 Rinehart103/120(A) 1,742,215 1/1930 Pigott.... 103/120(A) 2,955,541 10/1960Moore 103/120(A) Primary Examiner-Carlton R. Croyle AssistantExaminer-Wilbur J. Goodlin Attorney-Phillip A. Rein ABSTRACT: Thisinvention relates to variable capacity rotary hydraulic pump and/ormotor apparatus of the kind comprising, more particularly, a pump havinga variable discharge that will operate at a constant speed or a variablespeed motor driven by a constant volume of fluid. More particularly,this invention relates to a hydraulic pump or motor having rotat ing,engaging teeth members movable axially relative to each other withinrespective sleeve portions to expose variable meshing teeth areas toprovide the efficient and effective variable output apparatus of thisinvention. Additionally, this invention relates to variable outputapparatus having a control valve operably connected to opposite sides ofthe meshing gear teeth members so as to automatically maintain a givenadjusted position and operable to readily move the teeth membersrelative to each other when desired with said of the operating fluidpressure.

PATENTEU JUN28I9YI 3,588,295

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VARllARlLlE OUTPUT GEAR lPlUlVlllP R MOTOR APPARATUS In the prior artdevices, gear pumps have been long utilized in which there is aprovision for the movement between the gears of the pump in order tovary the volume discharge. For example, there are prior art devices inwhich one of the two pump elements is moved laterally relative to eachother thereby increasing or decreasing the area of gear tooth mesh andvarying the volume of discharge. These structures are satisfactory whereonly small pressures are developed but where the pump operates under arelatively high pressure differential, the radial thrust exerted by thefull fluid pressure makes it very difficult to maintain alignment in thegears and to adjust the pump while in use. Also, in the prior artdevices, it is found that on operating the meshing gear members for along period in one position, such produces extreme wear on the geartooth members wherein the same does not operate satisfactorily whenmoved to a different adjusted position due to fluid leakage axiallythereof. With the existing prior art structures, not only is itimpossible to provide for sensitive control of the capacity owing to thedifferent resistance offered to changes in capacity at different pointsand the rotation of the rotor, but rapid changes in capacity both duringoperation and for certain positions of the rotor during idle periods maybe impossible due to fluid locks.

In one preferred embodiment of this invention, a variable output gearapparatus is provided including a main pump means; fluid conveyancemeans secured to the pump means to supply and discharge fluid; and powermeans operably connected to the pump means for driving the same. It isobvious that this invention is referred to as a pump apparatus but thesame would additionally be a motor apparatus depending upon whetherfluid is provided under pressure to drive as a motor or whether a powermeans is used to drive the gear pump to create increased output pressurefrom a given input fluid. The pump means includes a housing means havinggear means therewithin operably controlled through a control valveassembly. The housing means includes a primary housing and a secondaryhousing. The primary housing has one end closed by a primary closureplate and a front end plate secured thereto through bolt members. Thesecondary housing is secured against the primary housing having itsother free end enclosed by a secondary closure plate and a rear endplate secured thereto as by bolt members. The gear means includes aninput gear assembly operably connected to an output gear assembly. Moreparticularly, the input gear assembly includes a main input shaftconnected to the power means and having a drive rotor assembly and adrive rotor sleeve member mounted about the input shaft. The input shaftis sealed at opposite ends and rotatably mounted on bearing members. Theoutput gear assembly includes an output shaft having an output rotorassembly thereon. The output rotor assembly includes a movable drivenrotor assembly connected to a control housing having the rotor assemblymovable axially within a driven rotors sleeve member. The control valveassembly ineludes an actuator member movable axially to control fluidmovement and pressure on opposite sides of the output gear assembly toautomatically maintain an adjusted position and, additionally operableto utilize output fluid pressure for moving the meshing gear membersrelative to each other. The fluid conveyance means includes inlet andoutlet conductor lines connected to the mating area of the output gearassembly and the input gear assembly. The power means may be a gasolineengine or an electric motor as required to rotate the input shaft on theinput gear assembly.

One object of this invention is to provide a variable output gear pumpapparatus overcoming the aforementioned disadvantages of the prior artdevices.

Another object of this invention is to provide a gear pump apparatushaving meshing gear members to provide for a variable output and controlmeans for readily moving the meshing gear members relative to each otherin an efficient and effective manner.

Still, one further object of this invention is to provide a variableoutput gear apparatus having mating gear members which are movable underprotective sleeve members so as to efficiently and effectively dischargethe desired fluid therefrom without the normal expectance loss on wearof the meshing tooth members.

Still, another object of this invention is to provide a variable outputgear apparatus which is readily assembled in an efficient and effectivemanner having plate members readily movable for replacing worn shims,seals, gear teeth members, and the like in a most efficient andeffective manner.

Still, one further object of this invention is to provide a variablegear apparatus usable as either a pump or a motor which is economical tomanufacture, highly efficient in operation, substantially maintenancefree, and simple to control and operate.

Various other objects, advantages, and features of the invention willbecome apparent to those skilled in the art from the followingdiscussion, which is taken in conjunction with the accompanyingdrawings, in which:

FIG. 1 is a perspective view of a variable output gear apparatus of thisinvention;

FIG. 2 is a longitudinal sectional view of the variable output gearapparatus of this invention having a power means removed therefrom;

FIG. 3 is an enlarged sectional view taken along line 3-3 in FIG. ll;

FIGS. 4, 5, and 6 are sectional views taken along respective lines 4-41,5-5, and 6-6 in FIG 2;

FIG. 7 is an enlarged fragmentary sectional view of the control valve ofthis invention;

FIG. 8 is a top plan view ofthe intermeshing gear structures and sleevemembers of this invention; and

FIG. 9 is a perspective view of the intermeshing gear structures andsleeve members of this invention.

The following is a discussion and description of preferred, specificembodiments of the new variable output gear apparatus of this invention,such being made with reference to the drawings, whereupon the samereference numerals are used to indicate the same or similar parts and/orstructure. It is to be understood that such discussion and descriptionis not to unduly limit the scope of the invention.

Referring to the drawings in detail and in particular to FIG. I, avariable output gear pump apparatus of this invention, indicatedgenerally at 112, includes a main pump means M having a fluid conveyancemeans 16 connected thereto to supply and direct fluid therefrom; and apower means 18 operably connected to the pump means 14. Although thisinvention will be described as a pump apparatus 12, it is obvious thatthe same can be supplied with a high pressure fluid so as to operate asa motor means instead of a pump means but such is clearly understood inthe art. The fluid conveyance means 16 includes an inlet fluid conductor19 and an opposed outlet fluid conductor 21 operable to supply anddeliver fluid therefrom as will become obvious. The power means 18 isillustrated as an electric motor 23 operable to drive the pump means 14of this invention. However, it is obvious that a gasoline engine or thelike can be used to drive a shaft member to provide the required powerinput.

The pump means 14 includes a main housing means 25 enclosing power gearmeans 26 and, additionally, having a control valve assembly 23 operablymounted within the interconnected portion of the gear means 26 toselectively and evenly control adjustment movements of the pumpapparatus l2 as will be explained.

' As shown in FIG. 2, the housing means 25 includes a primary housingassembly 29 interconnected as through bolt members 31 to a secondaryhousing assembly 33. More particularly, the primary housing assembly 29includes a primary housing 34 in abutting relationship to a secondaryhousing 36 of the secondary housing assembly 33 and having its open endclosed by a primary end plate 37 and a front end plate 39. The primaryhousing 34 is of an oblong cylindrical shape having cavities 41 toreceive portions of the gear means 26 and the control valve assembly 28therein. It is seen that the front end plate 39 is of an irregular shapesecured as by a plurality of bolt members 43 to the primary end plate 37and through holes 44 therein so as to be secured to the primary housing34. The front end plate 39 and the primary end plate 37 are providedwith a plurality of aligned openings to receive portions of the gearmeans 26 as will be explained in detail.

As shown in FIG. 2, the secondary housing assembly 33 includes thesecondary housing 36 abutting the primary housing 34 and having itsopposite end'enclosed by a secondary closure plate 47 and a rear endplate 49, respectively. More particularly, the elongated bolt members 31are extended through holes in the entire length of the secondary housing36 and anchored to the primary housing 34 with a sealing O-ring member53 therebetween. As seen in FIG. 1, the rear end plate 49 is of anirregular shape secured to the secondary closure plate 47 by boltmembers 54. It is seen that the rear end plate 49, secondary housing 36,and secondary closure plate 47 are provided with a plurality of alignedholes and openings therein to receive various elements of the gear means26 of this invention as will become obvious. It is seen that thesecondary housing 36 is of an oblong shape substantially similar to thatof the primary housing 34 and together therewith forms a compact, neatappearing structure as shown in FIG. 1.

The gear means 26 includes an input gear assembly 56 operably connectedto an output gear assembly 58 to achieve the desired variable gear pumpapparatus 12 of this invention. More particularly, as shown in FIG. 2,the input gear assembly 56 includes an elongated input shaft 59rotatably mounted within the housing means 25 and having a drive rotor61 and a drive rotor sleeve 63 connected thereto.

More particularly, the input power shaft 59 has one end mounted within ahole 64 in the secondary housing 36 secured thereto as by a lock nut 66and having the same rotatably mounted in a bearing member 68. A cupmember 70 and O- ring 71 seals the hole 64 to maintain fluid therein.The opposite end of the input power shaft 59 extends laterally of thefront end plate 39 and is provided with bushing members 73 and a bearingmember 74 for the easy rotation thereof. Also, a slinger and seal 76 isprovided adjacent the outer end of the input power shaft 59 to maintaina fluid seal therewithin. The seal area indicated at 77 is provided witha port opening to the input side of the pump to transfer any fluidleakage from chamber 41 and relieve pressure against the slinger andseal 76. A lock nut 78 is operable to maintain the proper axialpositioning adjustment of the input power shaft 59. The outer end of theinput power shaft 59 is provided with splines 79 so as to be readilyattachable to the drive shaft of the power means 18 to rotate same.

The drive rotor 61 is anchored to the power shaft 59 by a key 81 forrotation therewith and held against axial movement. The drive rotor 61is provided with a plurality of elongated teeth members 83 on the outerperiphery extended the entire length thereof.

As seen in FIGS. 2 and 9, the drive rotor sleeve 63 includes a basesection 85 having a plurality of elongated finger members 87, each of ashape to cover the area between adjacent ones of teeth members 83 on thedrive rotor 61. The base section 85 is axially movable on the powershaft 59 and rotatable with the drive rotor 61. It is seen that thefinger members 87 operate to seal the area between the teeth members 83not being presently used to aid in pump output and prevent fluidpressure loss. The base section 85 is provided with a groove 88 aboutits periphery for connection to the output gear assembly 58 by anarcuate guide member 89. Also, the base section 85 is provided with aleakage port 90 to connect an area 93 to the cavity 41 to prevent anyfluid lock.

The output gear assembly 58 includes an output shaft member 91 having anoutput rotor assembly 92 mounted thereon movable axially within anoutput sleeve member 94. The output shaft member 91 is provided withseal members 95 at opposite ends and conically shaped bores 97 toreceive anchoring and adjustment bolts 98 therewithin. Moreparticularly, each anchoring bolt 98 is provided with a threaded portionmounted within holes 101 in the rear end plate 49 and the front endplate 39 respectively. Adjusting nut members 103 are mounted on theanchoring bolts 101 and operable to anchor and center the output shaftmember 91 as required.

The driven sleeve member 94 is mounted on a bearing member 105 so as tobe rotatable about the output shaft member 91 but provided at a headportion 107 with a circumferential groove 108 adapted to receive alocking end plate member 109 therewithin which is secured as by a boltmember 110 to the secondary housing 36. The locking end plate member 109may be provided with a plurality of abutting shims for axial adjustmentof the driven sleeve member 94. This permits the driven sleeve member 94to rotate in conjunction with a driven rotor member 114 but the endplate member 109 restricts its axial movement therewith. The sleevemember 94 is formed with a plurality of axially extended finger members116 to fill up the space between teeth members on the driven rotormember 114 for efficient operation as will be explained.

The output rotor assembly 92 includes the axially movable driven rotormember 114 which abuts a connector housing 118, all of which areoperably mounted about the output shaft member 91 on a support cylinder119. The connector housing 118 is secured by a key member 121 to thesupport cylinder 119 mounted about the output shaft member 91 for axialmovement. The connector housing 118 is provided with an arcuate,laterally extended control valve housing 123 to receive the controlvalve assembly 28 therewithin as will be explained in detail. Thesupport cylinder 119 is provided with lock nuts 124 at opposite endsthereof to provide for the proper retention and spacing of the connectorhousing 118 and the driven rotor member 114. The end adjacent the drivenrotor member 114 is provided with a wear plate member 129 secured as bydowel pins 131 as the same will contact the rotating rotor member 114.

The driven rotor member 114 is provided with a central opening 133 so asto be rotatably mounted about its portion of the support cylinder 119.The outer periphery of the rotor member 114 is provided with a pluralityof teeth members 135 which are either; (1) engaging the teeth members 83on the drive rotor 61 or, (2) within the finger members 116 of thesleeve member 94. The driven rotor member 114 is held thereon by thelock nut 124 and axially movable in conjunction with the connectorhousing 118 about the output shaft member 91. Also, there is a spacer orbushing 136 mounted about the output shaft member 91 engageable with thesupport cylinder 119 to limit axial movement and to assure continuousengagement of the teeth members 83 and 135.

In order to better understand the relative movements of the interactingportions of the gear means 26 referring to FIGS. 2 and 9, it is seenthat rotation of the input power shaft 59 operates to rotate the driverotor 61 which has a portion thereof indicated at 134 engageable withthe driven rotor member 114. It is seen that only this portion 134 ofthe drive rotor 61 is revealed as the drive rotor sleeve 63 covers thesame so as to provide a limited meshing area. On rotation of the drivenrotor member 114, it is seen that the same is covered by the drivensleeve member 94 over all area except the meshing area. It is noted thatthe connector housing 118 does not rotate but is movably axially uponthe output shaft member 91. In fact, axial movement of the output gearassembly 58 upon its output shaft member 91 operates to increase ordecrease, or in other words, vary the meshing area of the drive rotor 61and the driven rotor member 114 to increase and decrease fluid outputtherefrom. It is seen that the novel actions of the drive rotor sleeveand the driven sleeve member 94 operates to control axial movement offluid therewithin so that the desired output is achieved without thenormal fluid losses inherent in the prior art structures. The meshingdrive rotor 61 and driven rotor member 114 are preferrably of a lengthfrom one-half to equal the diameter to provide the desired overallstrength.

As shown in FIG. 7, the control valve assembly 26 is mounted within anelongated, stepped bore 136 in the control valve housing 123 having anactuator control rod 136 extended laterally therefrom. Moreparticularly, the control valve assembly 26 includes a pressure outputassembly 139 operably connected to a control output assembly 141.

The pressure output assembly 139 includes in order, a plug member 143mounted within the bore 136 to receive fluid from the high pressureoutput side of the meshing gears; an actuator housing 144 threadablymounted within the bore 136; a control stem 146 mounted within a hole146 in the actuator housing 144; and a spring member 149 biasing thecontrol stem 146 to the closed condition. More particularly, theactuator housing 144 is provided with grooves 151 about its periphery toreceive sealing O-rings 153 therewithin and having the hole 146 providedwith a tapered seat portion 155 to receive the control stem 146. Thecontrol stem 146 is provided with a first guide portion 157;intermediate portion 159 of a smaller diameter; and an outer headportion 161 biased against the seat portion 155 by the spring member149. It is to be noted that the control stem 146 is movable axially soas to permit high pressure fluid to flow through an opening 162 to bedischarged into a high pressure fluid channel 164 for moving the variouselements of the gear means 26 as will be explained. The guide portion157 of the control stem 146 is mounted within a seal plug 166 having itsoutermost end extended laterally therefrom so as to be movable axiallyby the control rod 136.

The control output assembly 141 includes an extension of the actuatorhousing 144 mounted within the stepped bore 136 and sealed therein by anO-ring member 167. A central bore 169 of the actuator housing 144receives the actuator control rod 136 which is extended through a sealcap 171 and a plug 173. The seal cap 171 is biased by a spring member174 inwardly against a seat portion 176 in the actuator housing 144. Theactuator control rod 136 is provided with a block member 176 at theintermost end to contact the control stem 146 during its operation. Itis noted that fluid is movable within the actuator housing 144 about theactuator control rod 136 through the plug 173 about the seal cap 171 andthrough an opening 179 to the fluid input side when moving the gearmeans 26 as will be explained.

Also, the actuator control rod 136 is operable when pushed in to movethe control stem 146 to release the high pressure fluid through thefluid channel 164 to achieve axial movement of the output gear assembly56 in the operation to 'decrease the area of gear teeth meshing.

In use and operation of the variable output gear pump apparatus 12 ofthis invention, it is noted that the same is provided when acting as apump member with input low pressure fluid through the input conductor 19directed to the portion 134 ofthe intermeshing teeth of the drive rotorand the driven rotor member 114. The input power shaft 59 is driven bythe power means 16 such as a gasoline or electrical motor so as toinitially rotate the same at a given constantspeed with the variableoutput controlled by the amount of gear teeth meshing. In the adjustedposition of the power shaft 59 and the respective drive rotor 61 asshown in FIG. 2, it is seen that the drive rotor sleeve 63 extends oversubstantially the entire axial length of the teeth members on the driverotor 61 whereupon only a small portion is in engagement with thecomplimentary gear teeth on the driven rotor member 114. On operation inthis position, it is obvious that respective ones of the driven rotorsleeve 94 and the drive rotor sleeve 63 are rotatable with theirrespective rotors. On axial movement of the connector housing 116, it isseen that the same is interconnected through the guide member 69 to thedrive rotor sleeve 63 so that the same is movable axiallyrelative to thedrive rotor 61 as clearly shown in FIG. 9. Also, it is obvious that thedriven rotor member 114 is pulled with the connector housing 116 andsupport cylinder 119 axially out of the driven sleeve member 94. Whenthis happens, it is obvious that a greater amount of teeth members ofthe drive rotor 61 and the driven rotor member 114 are placed in themeshing engagement to increase the output of the pump apparatus of thisinvention as in the maximum output condition of FIGS. 6 and 9. It isobvious that such movement and resultant adjustment of variable outputof the pump apparatus can be achieved through axial movement of theconnector housing. Thus as seen in FIG. 9, the driven rotor member 114,the connector housing 116, the control valve housing 123, and the driverotor sleeve 63 move axially together as a unit.

It is noted that the efficient and effective operation of this inventionis achieved through the control valve assembly 26 whereupon the fluidpressure is being internally diverted in the pump apparatus 12 toprevent fluid lock and automatically achieve the desired output from theactuator control rod 136. In referring to FIG. 7 and assuming the gearmeans 26 in the position shown in FIG. 2, lets assume that the actuatorcontrol rod 136 is pulled outwardly on grasping of a knob member 160thereupon. This operates to pull the seal cap 171 outwardly off the seatportion 176 against the force of the spring member 174. On moving therod 136 outwardly, is is obvious that this allows the fluid from thecontrol area to move through the opening 179 for discharge to the inputside. When this is done, it is obvious that the high pressure fluidacting upon the opposite end of the connector housing 116 operates tomove the same to the right as viewed in FIG. 2 to increase the meshinggear teeth areas. After a sufficient movement is obtained, it is obviousthat the actuator control rod 136 can be released so that the system canthen neutralize and stabilize itself.

On assuming the full gear teeth meshing conditions of FIG. 6, let usassume that one now wishes to reduce the output of the pump apparatus12. First, the actuator control rod 136 is grasped and pushed inwardlyuntil the control block 1176 contacts the adjacent end of the controlstem 146. On moving the control stern 146 inwardly, it is obvious thatthe head portion 161 is moved off the seat portion against force of thespring member 149 to permit fluid pressure from the output side to flowthrough the fluid channel 164. It is obvious that this thereuponreleases fluid from one side of the connector housing 116 and provideshigh pressure on the opposite end of the connector housing 116 to aidmoving the same axially towards the condition of FIG. 2 to aid movingthe same axially towards the condition of FIG. 2 or however desired.

It is seen that the new and novel variable output gear pump apparatus ofthis invention is readily operable on attachment to the power means toachieve a variable fluid output from a given drive force. It is obviousthat the control means of this invention is operable to vary the amountof gear teeth meshing area to achieve the variable output as desired.Also, the new and novel interconnected cooperating sleeve members areoperable to achieve the efficient and effective overall fluid seal ofthis invention. It is seen that the control means of this invention isoperable in an efficient and effective manner to use operating fluidpressure as a means of moving and varying the area of gear teeth meshand automatically compensate itself to hold a given adjusted position.

The variable output gear pump apparatus of this invention is compact instructure, highly efficient in operation, easily adjustable and usablefor a variety of purposes, and constructed with features for easy repairand maintenance.

While the invention has been described in conjunction with preferredspecific embodiments thereof, it will be understood that thisdescription is intended to illustrate and not to limit the scope of theinvention, which is defined by the following claims.

I claim:

1. A variable capacity rotary fluid pressure machine of the characterdescribed, comprising;

a. pump means having a housing means enclosing a power gear means,

b. fluid conveyance means connected to said housing means operable tosupply to and direct fluid from said power gear means,

c. power means connected to said power gear means,

d. said gear means having an input gear assembly operably connected toan output gear assembly,

said input gear assembly having an input shaft connected to said powermeans rotatably mounted in said housing means, a drive rotor secured tosaid input shaft, and a drive rotor sleeve mounted about said inputshaft and axially movable thereon to conceal and reveal portions of saiddrive rotor,

. said output gear assembly having an output shaft member mounted withinsaid housing means, an output rotor assembly rotatable on and axiallymovable on said output shaft, and a driven sleeve member rotatablymounted on said output shaft,

. said drive rotor and said output rotor assembly having portionsthereof in engagement to impart pressure to fluid from said fluidconveyance means, and said output rotor assembly movable axiallyrelative said drive rotor to vary said portions in engagement toselectively increase or decrease the output of said fluid pressuremachine,

. said output rotor assembly having a connector housing secured to asupport cylinder positioned in abutting relationship to a driven rotormember rotatably mounted on said support cylinder whereby said connectorhousing cooperates with said driven sleeve member to maintain fluidwithin the mating areas of said gear teeth members,

i. said driven sleeve member having a head section integral with aplurality of axially extended fingers and a lock plate member secured tosaid housing means engageable with said head section to permit rotationbut prevent axial movement of said driven sleeve member, and

j. said drive rotor sleeve having a base section having a fluid leakageport therein connected by an arcuate guide member to said connectorhousing for independent rotational movement on said input shaft andaxial movement with said output rotor assembly.

2. A fluid pressure machine as described in claim 1, wherein;

a. said output rotor assembly having a continuous wear member releasablysecured to said connector housing abutting said driven rotor, and

said housing means having fluid control chambers on opposite sides ofsaid output rotor assembly to aid in axial. movement thereof on varyingoutput of said fluid presing;

sure machine by utilizing the output fluid pressure as the moving force.A fluid pressure machine as described in claim 1, includsaid output gearassembly having a connector housing and a driven rotor member mounted ona support cylinder,

. said connector housing having a control housing with an elongatedaxially extended bore therethrough,

a control valve assembly mounted within said bore moved with saidconnector housing having a control rod movable within a control outputassembly operably connected to a pressure output assembly, and

. said pressure output assembly to receive high pressure said controloutput assembly having a seal cap mounted about said control rod biasedby a spring member into sealing engagement with an abutting actuatorhousing to prevent fluid flow thereabout, and

. said control rod having an inner block engageable with said seal capon outward movementto move said seal cap into an open condition topermit fluid flow from the outer end of said connector housing toexhaust whereby the existing high pressure fluid against the inner endofsaid connector housing acts to increase the area of meshing gear teethand resultant output.

A fluid pressure machine as described in claim 4,

wherein;

said control rod movable inwardly to move said control stem by saidblock to the open condition to utilize high pressure fluid moving saidoutput gear assembly to decrease the area of meshing gear teeth andresultant output.

